US4623305A - Device for pumping oil - Google Patents

Device for pumping oil Download PDF

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Publication number
US4623305A
US4623305A US06/744,039 US74403985A US4623305A US 4623305 A US4623305 A US 4623305A US 74403985 A US74403985 A US 74403985A US 4623305 A US4623305 A US 4623305A
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United States
Prior art keywords
screw
pressure chamber
balancing
pump
drive
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Expired - Lifetime
Application number
US06/744,039
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English (en)
Inventor
Lars Segerstrom
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STC PLC
IMO AB
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IMO AB
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Assigned to IMO AB VASTBERGA ALLE, A CORP. OF SWEDEN reassignment IMO AB VASTBERGA ALLE, A CORP. OF SWEDEN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SEGERSTROM, LARS H.
Application granted granted Critical
Publication of US4623305A publication Critical patent/US4623305A/en
Assigned to STC PLC reassignment STC PLC ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: INTERNATIONAL STANDARD ELECTRIC CORPORATION, A DE CORP.
Assigned to IMO INDUSTRIES INC. reassignment IMO INDUSTRIES INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANK OF NOVA SCOTIA, THE
Assigned to BANK OF NOVA SCOTIA, THE reassignment BANK OF NOVA SCOTIA, THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMERICAN ENTERPRISES MPT CORP., AMERICAN ENTERPRISES MPT HOLDINGS, L.P., AMERIDRIVES INTERNATIONAL, L.P., CLFX CORPORATION, COLFAX CORPORATION, CONSTELLATION PUMPS CORPORATION, FORMSPRAG LLC, IMO HOLDINGS, INC., IMO INDUSTRIES, INC., INCOM TRANSPORTATION, INC., NETZCH USA CORPORATION, NUTTALL GEAR LLC, WARNER ELECTRIC FINANCE COMPANY, INC., WARNER ELECTRIC HOLDING, INC., WARNER ELECTRIC INTERNATIONAL HOLDING, INC., WARNER ELECTRIC TECHNOLOGIES, INC., WARNER ELECTRIC, INC., WARREN PUMPS INC.
Anticipated expiration legal-status Critical
Assigned to IMO INDUSTRIES, INC., COLFAX CORPORATION, CONSTELLATION PUMPS CORPORATION, AMERIDRIVES INTERNATIONAL, L.P., NETZCH USA CORPORATION, CLFX CORPORATION, INCOM TRANSPORTATION, INC., AMERICAN ENTERPRISES MPT HOLDINGS, L.P., NUTTALL GEAR LLC, WARREN PUMPS INC., WARNER ELECTRIC TECHNOLOGY, INC., WARNER ELECTRIC FINANCE COMPANY, INC., FORMSPRAG LLC, IMO HOLDINGS, INC., WARNER ELECTRIC, INC., WARNER ELECTRIC INTERNATIONAL HOLDING, INC., WARNER ELECTRIC HOLDING, INC., AMERICAN ENTERPRISES MPT CORP. reassignment IMO INDUSTRIES, INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: THE BANK OF NOVA SCOTIA
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/008—Pumps for submersible use, i.e. down-hole pumping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump

Definitions

  • the present invention relates to a device preferably used for pumping oil or other fluid from a drill hole in the ground, the device including a pump with a driving motor under it and connected to the pump, which are lowered into the drill hole.
  • the pump comprises a hydraulic screw machine including a screw array including a drive screw and at least one running screw co-acting therewith, arranged in a housing with the drive screw connected to a shaft extending outside the housing on the low pressure side of the device, the screws being provided on the low pressure side of the screw array with mutually co-acting balancing pistons adapted for hydraulically balancing the screws against axially acting forces.
  • centrifugal pumps In pumping such as crude oil from deep drill holes in the ground it is known to use centrifugal pumps and piston pumps lowered in the holes.
  • the use of such pumps is associated with certain disadvantages, however.
  • the disadvantages limiting the use of centrifugal pumps are that they have long extension in the longitudinal direction of the drill hole, since they must be provided with several stages connected in series for pumping up from great depths, and also that they have relatively poor efficiency when used for high oil viscosities.
  • a disadvantage limiting the use of piston pumps is that they can only be used at relatively small depths since piston stroke will otherwise be unacceptably long.
  • One object of the present invention is to provide a device preferably for pumping oil or other fluid up from a drill hole in the ground, said device including a screw machine which can be used at very large depths and there take up large hydrostatic pressure, and which also can pump liquid with extremely large inlet and outlet pressures, with different viscosities and with relatively large gas content, the machine having a relatively small axial extension and a rotation of direction which may be temporarily reversed for cleaning a strainer or the like covering the inlet of the machine.
  • FIG. 1 is a schematic, partially cut-away side view of a device in accordance with the invention in use in a drill hole in the ground, and
  • FIG. 2 is a side view, showing planes cutting each other at right angles, of a screw machine included in the device illustrated in FIG. 1.
  • a drill hole made in the ground is denoted by B in FIG. 1.
  • a typical drill hole may be 12,7 cm in diameter and 5,000 m deep.
  • a pipe 1 is driven into the drill hole B, which is partially filled with such as crude oil and gas. Under its prevailing pressure oil is supplied to the interior of the pipe 1 via openings 1a at its lower end.
  • This equipment includes an electric motor 3 with power supply from the means 2 via a cable 6, a hydraulic screw machine 4 rigidly bolted to the motor and acting as a pump, as well as a pipe string 5 bolted to the pump and consisting of a plurality of jointed pipes extending to the means 2.
  • FIG. 2 A central portion of the pump 4 is illustrated in FIG. 2.
  • the end members denoted by 7 and 8 of the pump are bolted to the motor 3 and the pipe string 5, respectively, as illustrated in FIG. 1.
  • the end members 7 and 8 are threaded into the pipe housing 9.
  • the end member 7 is provided with an opening 10 disposed directly opposite a radial inlet opening 11 to the interior of the housing 9, and the opening 10 is covered by a strainer 12 attached to the circular surface of the member 7.
  • the pump housing 9 is provided with a passage formed by three mutually intersecting cylindrical bores, the central one of which accommodates a drive screw 13, and both the outer bores accommodate running screws meshing with the drive screw, only one running screw 14 being illustrated in FIG. 2.
  • the passage formed by the bores extends with a constant cross-section through the entire housing 9 from one end to the other, one end being open towards a space 16 between the pump and motor and the other end being open towards a space 15 between the pump and the pipe string 5.
  • the drive screw 13 is made conventionally with convex threads and the running screws 14 with concave threads, the crests of the threads being sealingly surrounded by the bores with the threads sealing against each other. Between the threads and the housing there are thus formed mutually sealed chambers wherein oil is conveyed through the screw array.
  • the openings 10, 11 are at the downward end of the housing 9 in FIG. 1, which is the left-hand end in FIG. 2, and the screws rotate such that the oil is conveyed through the openings 10, 11 which communicate with the space between the pipe 1 and pump 4, the oil coming in radially and being conveyed by the screws towards the space 15 and further up through the pipe string 5 for further conveying via the means 2.
  • the unthreaded end portions of the running screws 14 form balancing pistons 22, which radially engage against the walls of the outer bores and form narrow gaps towards the axial surface of the drive screw end portion.
  • the drive screw 13 is provided with a balancing piston 24 of the same diameter as the crests thereof and engaging radially against the wall of the central bore.
  • the piston 24 is located outside the pistons 22 and its face 23 towards the drive screw thread is situated adjacent the faces 25 of the pistons 22 remote from the running screw threads so that a variable gap A is formed between them.
  • the drive screw 13 continues outside the balancing piston 24 with a shaft 20 which is journalled in a bearing 21 arranged in a part of the housing 9 formed as a cover 30.
  • the shaft 20 is provided with splines for enabling removable coupling to the output shaft of the electric motor 3.
  • a balancing collar 26 is attached to the drive screw 13 adjacent the face of the balancing piston 24 remote from the drive screw.
  • the inlet of the first pressure chamber 28 is in communication with the pump outlet at 15 via an axial bore 36 through the drive screw and a radial bore 38 communicating therewith through the drive screw and opening out into the pressure chamber 28 at the axial surface of the drive screw.
  • the outlet of the first pressure chamber 28 consists of a variable gap C between the wear rings 27 and 29.
  • the inlet to the second pressure chamber 32 comprises a through, axial hole 34 in the balancing collar 26 and the inlet at the gap C, which thus connects the first and second pressure chambers, while the outlet of the second pressure chamber 32 consists of the gap A.
  • Oil is introduced to the first pressure chamber 28 via the bores 36 and 38 at a pressure substantially corresponding to the outlet pressure at 15 of the pump, this pressure also acting on the substantially radial end surfaces of the screws 13 and 14, to the right in FIG. 2, and strives to displace the screws to the left in this FIGURE.
  • the left, annular side surface of the collar 26, between the axial surface 13 of the drive screw and the wear ring 29, is greater than the combined radial sectional surfaces of the three bores in the housing 9, and therefore the oil pressure acting on this side surface strives to displace the drive screw to the right.
  • the gap C which forms a hydrostatic bearing between the washer 26 and the housing part 30, will vary in width in response to the pressure in the pressure chamber 28 and in response to the axial forces acting on the drive screw. For an increased axial force to the left on the drive screw, the pressure in the pressure chamber 28 will increase, since the gap C becomes less, which results in that the drive screw via the collar 26 strives to return to the right.
  • the hole 34 is dimensioned such that the pressure in the pressure chamber 32 will always be so much greater than the axial pressure acting on the running screws 14 that the output flow gap A between the balancing pistons 22 and 24 is maintained and mechanical contact between their surfaces 23 and 25 is avoided.
  • the dimension of the hole 34 may be regulatable for adjusting the pump to different operating conditions.
  • the screw machine in accordance with the invention has been described above in conjunction with pumping oil up out of a drill hole B, the electric motor 3 driving the screw array 13, 14 in one direction of rotation.
  • the rotational direction of the electric motor is reversible for temporarily being able to reverse the rotational direction of the screw array so that oil is pumped in through the outlet (at 15) and out through the inlet (at 10, 11).
  • Foreign matter which may have collected on the outside of the strainer 12, making it more difficult, or even preventing oil from being sucked in through the inlet 10, 11, is thus forced away from the strainer so that it becomes clear again. Due to the balancing described above, the screw array will not be subjected to unpermitted, large axial stresses during its rotation in the opposite direction.
  • the screw machine described above may be used as a drill hole pump, in which the axial forces acting on the drive and running screws are balanced for ensuring an effective and reliable mode of operation under the special conditions existing in a deep drill hole.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Details Of Reciprocating Pumps (AREA)
US06/744,039 1984-06-20 1985-06-12 Device for pumping oil Expired - Lifetime US4623305A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8403316A SE463682B (sv) 1984-06-20 1984-06-20 Hydraulisk skruvmaskin, foeretraedesvis utnyttjad som pump avsedd att nedsaenkas i ett borrhaal
SE8403316 1984-06-20

Publications (1)

Publication Number Publication Date
US4623305A true US4623305A (en) 1986-11-18

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ID=20356307

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Application Number Title Priority Date Filing Date
US06/744,039 Expired - Lifetime US4623305A (en) 1984-06-20 1985-06-12 Device for pumping oil

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Country Link
US (1) US4623305A ( )
EP (1) EP0168366B1 ( )
JP (1) JPS6114491A ( )
AT (1) ATE45613T1 ( )
DE (1) DE3572382D1 ( )
SE (1) SE463682B ( )

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003029610A1 (en) * 2001-09-28 2003-04-10 Pradeep Dass Downhole multi-phase twin screw pump
DE10238456C1 (de) * 2002-08-22 2003-10-02 Leistritz Ag Pumpe zur Förderung von Erdöl aus Tiefbohrungen
US20070007013A1 (en) * 2005-07-07 2007-01-11 Baker Hughes Incorporated Downhole gas compressor
USRE39597E1 (en) 2001-07-02 2007-05-01 Carrier Corporation Variable speed drive chiller system
US7370697B1 (en) * 2003-12-29 2008-05-13 Wood Group Esp, Inc. Thrust section wear preventor
CN101864932A (zh) * 2010-05-28 2010-10-20 盘锦三阳石油科技发展有限公司 大排量电潜螺杆泵采油设备
CN103835681A (zh) * 2014-03-13 2014-06-04 东营市一旭石油装备有限公司 一种潜油电机带动的往复抽油装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4669961A (en) * 1986-05-06 1987-06-02 Hughes Tool Company Thrust balancing device for a progressing cavity pump
DE9215639U1 (de) * 1992-11-12 1994-03-17 Zimmer Johannes Einrichtung zur Zuführung fließfähiger Substanzen an eine substanzverbrauchende Maschine
NL9400708A (nl) * 1994-04-29 1995-12-01 Houttuin Technology N V Werkwijze en inrichting voor het oppompen van vloeistof uit de aardkorst.
ITAN20130102A1 (it) * 2013-05-30 2014-12-01 Marzocchi Pompe S P A Pompa o motore idraulico ad ingranaggi a dentatura elicoidale con sistema idraulico per il bilanciamento di forze assiali.
WO2016037299A1 (zh) * 2014-09-09 2016-03-17 赵锡寰 带井下驱动转换装置的潜没式抽油泵机组

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1593820A (en) * 1925-02-25 1926-07-27 Standard Oil Co Well-pumping apparatus
US2095167A (en) * 1935-02-26 1937-10-05 Burghauser Franz Screw pump
US2286365A (en) * 1940-04-16 1942-06-16 Lane Jack Well pump
US2455022A (en) * 1944-08-08 1948-11-30 Benjamin F Schmidt Submersible double-acting fluid piston deep well pump
US2590561A (en) * 1947-12-10 1952-03-25 Montelius Carl Oscar Josef Screw pump
US2592476A (en) * 1948-02-07 1952-04-08 Laval Steam Turbine Co Series arrangement of positive and nonpositive screw pumps
US2737119A (en) * 1951-05-23 1956-03-06 Perfect Circle Corp Pumping apparatus
US3391643A (en) * 1966-02-07 1968-07-09 Warren Pumps Inc Sub-surface pump
DE1930839A1 (de) * 1969-06-18 1970-12-23 Allweiler Ag Einrichtung zum Ausgleichen der Axialkraefte an Wellen von als Pumpe oder als Motor wirkenden Rotationsmaschinen
US4028025A (en) * 1975-05-02 1977-06-07 Aktiebolaget Imo Industre Screw pump
US4131400A (en) * 1976-04-27 1978-12-26 Aktiebolaget Imo-Industri Hydraulic rotary screw machine with axial balancing piston
GB2023739A (en) * 1978-06-28 1980-01-03 Allweiler Ag Rotary positive-displacement fluid-machines
US4242067A (en) * 1977-09-15 1980-12-30 Imo-Industri Aktiebolag Hydraulic screw machine with balance plunger
US4547135A (en) * 1982-12-11 1985-10-15 ALLWEILER AG Aktiengesellschaft Motor-pump unit

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH354333A (de) * 1956-10-12 1961-05-15 Licencia Talalmanyokat Schraubenpumpe mit umkehrbarer Drehrichtung
US3677665A (en) * 1971-05-07 1972-07-18 Husky Oil Ltd Submersible pump assembly
JPS491842U ( ) * 1972-04-07 1974-01-09
DE3010606A1 (de) * 1980-03-20 1981-10-15 Allweiler Ag, 7760 Radolfzell Schraubenspindelpumpe
DE3106483A1 (de) * 1981-02-21 1982-09-09 Allweiler Ag, 7760 Radolfzell Stopfbuechsloses pumpenaggregat

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1593820A (en) * 1925-02-25 1926-07-27 Standard Oil Co Well-pumping apparatus
US2095167A (en) * 1935-02-26 1937-10-05 Burghauser Franz Screw pump
US2286365A (en) * 1940-04-16 1942-06-16 Lane Jack Well pump
US2455022A (en) * 1944-08-08 1948-11-30 Benjamin F Schmidt Submersible double-acting fluid piston deep well pump
US2590561A (en) * 1947-12-10 1952-03-25 Montelius Carl Oscar Josef Screw pump
US2592476A (en) * 1948-02-07 1952-04-08 Laval Steam Turbine Co Series arrangement of positive and nonpositive screw pumps
US2737119A (en) * 1951-05-23 1956-03-06 Perfect Circle Corp Pumping apparatus
US3391643A (en) * 1966-02-07 1968-07-09 Warren Pumps Inc Sub-surface pump
DE1930839A1 (de) * 1969-06-18 1970-12-23 Allweiler Ag Einrichtung zum Ausgleichen der Axialkraefte an Wellen von als Pumpe oder als Motor wirkenden Rotationsmaschinen
US4028025A (en) * 1975-05-02 1977-06-07 Aktiebolaget Imo Industre Screw pump
US4131400A (en) * 1976-04-27 1978-12-26 Aktiebolaget Imo-Industri Hydraulic rotary screw machine with axial balancing piston
US4242067A (en) * 1977-09-15 1980-12-30 Imo-Industri Aktiebolag Hydraulic screw machine with balance plunger
GB2023739A (en) * 1978-06-28 1980-01-03 Allweiler Ag Rotary positive-displacement fluid-machines
US4547135A (en) * 1982-12-11 1985-10-15 ALLWEILER AG Aktiengesellschaft Motor-pump unit

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE39597E1 (en) 2001-07-02 2007-05-01 Carrier Corporation Variable speed drive chiller system
US20050002812A1 (en) * 2001-09-28 2005-01-06 Pradeep Dass Method of adapting a downhole multi-phase twin screw pump for use in wells having a high gas content and a downhole multi-phase twin screw pump
US7093665B2 (en) 2001-09-28 2006-08-22 Pradeep Dass Method of adapting a downhole multi-phase twin screw pump for use in wells having a high gas content and a downhole multi-phase twin screw pump
WO2003029610A1 (en) * 2001-09-28 2003-04-10 Pradeep Dass Downhole multi-phase twin screw pump
DE10238456C1 (de) * 2002-08-22 2003-10-02 Leistritz Ag Pumpe zur Förderung von Erdöl aus Tiefbohrungen
US7370697B1 (en) * 2003-12-29 2008-05-13 Wood Group Esp, Inc. Thrust section wear preventor
US20070007013A1 (en) * 2005-07-07 2007-01-11 Baker Hughes Incorporated Downhole gas compressor
US7401655B2 (en) * 2005-07-07 2008-07-22 Baker Hughes Incorporated Downhole gas compressor
US20080271886A1 (en) * 2005-07-07 2008-11-06 Baker Hughes Incorporated Downhole Gas Compressor
US7644770B2 (en) 2005-07-07 2010-01-12 Baker Hughes Incorporated Downhole gas compressor
CN101864932A (zh) * 2010-05-28 2010-10-20 盘锦三阳石油科技发展有限公司 大排量电潜螺杆泵采油设备
CN101864932B (zh) * 2010-05-28 2013-01-09 盘锦三阳石油科技发展有限公司 大排量电潜螺杆泵采油设备
CN103835681A (zh) * 2014-03-13 2014-06-04 东营市一旭石油装备有限公司 一种潜油电机带动的往复抽油装置

Also Published As

Publication number Publication date
SE8403316D0 (sv) 1984-06-20
EP0168366A1 (en) 1986-01-15
ATE45613T1 (de) 1989-09-15
JPS6114491A (ja) 1986-01-22
SE463682B (sv) 1991-01-07
DE3572382D1 (en) 1989-09-21
EP0168366B1 (en) 1989-08-16
SE8403316L (sv) 1985-12-21

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